CN104246386A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- CN104246386A CN104246386A CN201380020042.5A CN201380020042A CN104246386A CN 104246386 A CN104246386 A CN 104246386A CN 201380020042 A CN201380020042 A CN 201380020042A CN 104246386 A CN104246386 A CN 104246386A
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- Prior art keywords
- air conditioner
- heat exchanger
- temperature
- indoor
- load
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0068—Indoor units, e.g. fan coil units characterised by the arrangement of refrigerant piping outside the heat exchanger within the unit casing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
- F24F2003/1446—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/50—Load
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2104—Temperatures of an indoor room or compartment
Abstract
When a dehumidifying operation is carried out, the coefficient of performance (COP) deteriorates. An air conditioner according to the present invention comprises an indoor heat exchanger, which has an auxiliary heat exchanger (20) and a main heat exchanger (21) disposed on the downstream side of the auxiliary heat exchanger (20). While operating in a predetermined dehumidifying operation mode, all of the liquid refrigerant supplied to the auxiliary heat exchanger (20) evaporates partway through the auxiliary heat exchanger (20). As a result, only a portion of the upstream side of the auxiliary heat exchanger (20) is an evaporation region, and the area on the downstream side of the evaporation region for the auxiliary heat exchanger (20) is a superheating region. If the load is high when the dehumidifying operation is selected and operation begins, the air conditioner starts the cooling operation and then switches to the dehumidifying operation in accordance with a decrease in the load.
Description
Technical field
The present invention relates to and carry out the air conditioner operated that dehumidifies.
Background technology
In air conditioner in the past, there is a kind of air conditioner, at the rear side configuration secondary unit of its main heat exchanger, dehumidify locally by means of only secondary unit makes cold-producing medium evaporate, even if thus the cooling capacity hour that the difference of (when the rotating speed of compressor is low), such as room temperature and design temperature is enough little, required when low load also can dehumidify.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 9-14727 publication
Summary of the invention
The problem that invention will solve
But in this air conditioner, when indoor temperature height, if take only by the mode that secondary unit cools from the outset, then cooling capacity is not enough, can not the temperature in room be reduced immediately.
Therefore, when carrying out dehumidifying running, there is COP (Energy Efficiency Ratio) and to be deteriorated such problem.
Therefore, the object of the invention is to, provide a kind of air conditioner, the impact that the COP for the running that dehumidifies can be made to be deteriorated is Min..
For solving the means of problem
The air conditioner of a first aspect of the present invention possesses refrigerant loop compressor, outdoor heat converter, expansion valve and indoor heat converter coupled together, carry out using whole described indoor heat converter as the cooling operation in evaporation territory with using a part for indoor heat converter as the dehumidifying running in evaporation territory, the feature of described air conditioner is, when starting running when selecting dehumidifying running, load is large, start after cooling operation, be correspondingly switched to dehumidify with the reduction of load and operate.
According to this air conditioner, when when select dehumidifying running and start running time load large, even if due to when cooling operation the temperature of heat exchanger also low, thus can dehumidify fully, therefore, by starting cooling operation, can carry out expeditiously dehumidifying and freezing simultaneously.Further, when indoor temperature reduce and load diminish time, when cooling operation, become because evaporating temperature uprises and cannot dehumidify, therefore at that time carve being switched to dehumidifying running.Thereby, it is possible to the impact making the COP for the running that dehumidifies be deteriorated is Min..
Air conditioner according to a second aspect of the invention, is characterized in that, in the air conditioner of first aspect, the difference according to indoor temperature and design temperature detects load.
According to this air conditioner, load can be detected according to the difference of indoor temperature and design temperature.
Air conditioner according to a third aspect of the invention we, is characterized in that, first or second aspect air conditioner in, the frequency according to described compressor detects load.
According to this air conditioner, load can be detected according to the frequency of compressor.
Air conditioner according to a forth aspect of the invention, is characterized in that, in the air conditioner of the either side in the first to the third aspect, after beginning cooling operation, in evaporating temperature lower than not being switched to dehumidifying running when set point of temperature.
According to this air conditioner, when load diminishes to setting, because evaporating temperature is lower than setting, also can dehumidify even if be not therefore switched to dehumidifying running from cooling operation.
Invention effect
As described in the above description, according to the present invention, following effect can be obtained.
According to the invention of first aspect, when load is large, though due to when cooling operation the temperature of heat exchanger also low, thus can dehumidify fully, therefore, by start cooling operation, can carry out expeditiously dehumidifying and freezing simultaneously.Further, when indoor temperature reduce and load diminish time, when cooling operation, become because evaporating temperature uprises and cannot dehumidify, therefore at that time carve being switched to dehumidifying running.Thereby, it is possible to the impact making the COP for the running that dehumidifies be deteriorated is Min..
According to the invention of second aspect, load can be detected according to the difference of indoor temperature and design temperature.
According to the invention of the third aspect, load can be detected according to the frequency of compressor.
According to the invention of fourth aspect, when load diminishes to setting, because evaporating temperature is lower than setting, also can dehumidify even if be not therefore switched to dehumidifying running from cooling operation.
Accompanying drawing explanation
Fig. 1 is the loop diagram of the refrigerant loop of the air conditioner that embodiments of the present invention are shown.
Fig. 2 is the general profile chart of the indoor set of the air conditioner that embodiments of the present invention are shown.
Fig. 3 is the figure of the structure that indoor heat converter is described.
Fig. 4 is the figure of the control part of the air conditioner that embodiments of the present invention are described.
Fig. 5 shows an example of changes in flow rate when to change aperture in expansion valve.
Fig. 6 is the figure of the action of the air conditioner that embodiments of the present invention are described.
Detailed description of the invention
Below, the embodiment of air conditioner 1 of the present invention is described.
The overall structure > of < air conditioner 1
As shown in Figure 1, the air conditioner 1 of present embodiment possesses: indoor set 2 disposed in the interior; With off-premises station 3 disposed in the outdoor.Further, air conditioner 1 possesses refrigerant loop compressor 10, cross valve 11, outdoor heat converter 12, expansion valve 13 and indoor heat converter 14 coupled together.In refrigerant loop, through cross valve 11, outdoor heat converter 12 is connected with the outlet of compressor 10, expansion valve 13 is connected with this outdoor heat converter 12.Further, one end of indoor heat converter 14 is connected with expansion valve 13, through cross valve 11, the suction inlet of compressor 10 is connected with the other end of this indoor heat converter 14.Indoor heat converter 14 has secondary unit 20 and main heat exchanger 21.
Air conditioner 1 can carry out cooling operation pattern, the dehumidifying operation mode of regulation and the running of heating mode of operation, and can utilize remote controller carry out to select arbitrary running running start operation carry out running handover operation or operate shut-down operation.In addition, utilize remote controller and the design temperature of indoor temperature can be set or changed the air quantity of indoor set 2 by the rotating speed changing indoor fan.
Under the dehumidifying operation mode of cooling operation pattern and regulation, as shown in illustrated solid arrow, form following kind of refrigeration cycle or dehumidifying circulation: the cold-producing medium of discharging from compressor 10 sequentially flows to outdoor heat converter 12, expansion valve 13, secondary unit 20 and main heat exchanger 21 from cross valve 11, and the cold-producing medium through main heat exchanger 21 gets back to compressor 10 by cross valve 11.That is, outdoor heat converter 12 plays a role as condenser, and indoor heat converter 14 (secondary unit 20 and main heat exchanger 21) plays a role as evaporimeter.
On the other hand, under heating mode of operation, by switching cross valve 11, thus formed as shown in diagram dotted arrow and following heat circulation: the cold-producing medium of discharging from compressor 10 sequentially flows to main heat exchanger 21, secondary unit 20, expansion valve 13 and outdoor heat converter 12 from cross valve 11, and the cold-producing medium through outdoor heat converter 12 gets back to compressor 10 by cross valve 11.That is, indoor heat converter 14 (secondary unit 20 and main heat exchanger 21) plays a role as condenser, and outdoor heat converter 12 plays a role as evaporimeter.
Indoor set 2 has the suction inlet 2a of room air at upper surface, has the blow-off outlet 2b of idle call air in front lower.In indoor set 2, be formed with air flow circuit from suction inlet 2a towards blow-off outlet 2b, be configured with the indoor fan 16 of indoor heat converter 14 and cross-flow type at this air flow circuit.Therefore, when indoor fan 16 rotates, room air is inhaled in indoor unit 1 from suction inlet 2a.In the front side of indoor set 2, the suction air from suction inlet 2a flows to indoor fan 16 side by secondary unit 20 and main heat exchanger 21.On the other hand, in the rear side of indoor set 2, the suction air from suction inlet 2a flows to indoor fan 16 side by main heat exchanger 21.
As mentioned above, indoor heat converter 14 has: secondary unit 20; With main heat exchanger 21, when operating under the dehumidifying operation mode in cooling operation pattern and regulation, described main heat exchanger 21 is configured in the downstream of secondary unit 20.Main heat exchanger 21 has: preceding heat exchanger 21a, and it is configured in the front face side of indoor set 2; With back-surface heat exchanger 21b, it is configured in the rear side of indoor set 2, and this heat exchanger 21a, 21b are to be configured to around the mode of indoor fan 16 shape of falling V.Further, secondary unit 20 is configured in the front of preceding heat exchanger 21a.Secondary unit 20 and main heat exchanger 21 (preceding heat exchanger 21a, back-surface heat exchanger 21b) possess heat-exchange tube and multi-disc fin respectively.
As shown in Figure 3, under the dehumidifying operation mode of cooling operation pattern and regulation, from be configured in secondary unit 20 below end near liquid inlet 17a liquid refrigerant is provided, this liquid refrigerant provided flows in the mode of the upper end close to secondary unit 20.Further, flow out from the outlet 17b near the upper end being configured in secondary unit 20 and flow to branch 18a.Be provided to the inferior portion of preceding heat exchanger 21a, upper section and back-surface heat exchanger 21b from three of main heat exchanger 21 entrance 17c respectively at the cold-producing medium of branch 18a branch, then, flow out from outlet 17d and converge at merging part 18b.In addition, under heating mode of operation, cold-producing medium flows along direction contrary to the above.
Further, according to air conditioner 1, during running under the dehumidifying operation mode carrying out specifying, the liquid refrigerant provided from the liquid inlet 17a of secondary unit 20 all evaporates the way of secondary unit 20.Therefore, the scope of the part near the liquid inlet 17a of only secondary unit 20 is the evaporation territory of liquid refrigerant evaporates.Therefore, when operating under the dehumidifying operation mode specified, in indoor heat converter 14, only a part for the upstream side of secondary unit 20 is evaporation territory, and scope and the main heat exchanger 21 in the downstream in the evaporation territory of secondary unit 20 were thermal domain.
Further, the cold-producing medium that the mistake thermal domain near the upper end of secondary unit 20 flows through flows through the inferior portion of the preceding heat exchanger 21a configured at the downwind side of the inferior portion of secondary unit 20.Therefore, from the suction air of suction inlet 2a, the air cooled in the evaporation territory of secondary unit 20 is blown from blow-off outlet 2b after preceding heat exchanger 21a is heated.On the other hand, from in the suction air of suction inlet 2a, be blown from blow-off outlet 2b with the temperature roughly the same with indoor temperature with the air that heat exchanger 21b flows through overleaf with the air that preceding heat exchanger 21a flows through in the mistake thermal domain of secondary unit 20.
According to air conditioner 1, as shown in Figure 1, be provided with evaporating temperature sensor 30 at off-premises station 3, described evaporating temperature sensor 30 detects evaporating temperature in the downstream of expansion valve 13 in refrigerant loop.Further, be provided with at indoor set 2: indoor temperature transmitter 31, it detects indoor temperature (temperature from the suction air of the suction inlet 2a of indoor set 2); With Indoor Thermal exchange temperature sensor 32, its situation complete to liquid refrigerant evaporates in secondary unit 20 detects.
As shown in Figure 3, Indoor Thermal exchange temperature sensor 32 is configured in the downwind side near the upper end of secondary unit 20.Further, the mistake thermal domain near the upper end of secondary unit 20, the suction air from suction inlet 2a is cooled hardly.Therefore, when the temperature detected by Indoor Thermal exchange temperature sensor 32 is roughly the same with the indoor temperature detected by indoor temperature transmitter 31, following situation can be detected: evaporate in the midway of secondary unit 20, the scope near the upper end of secondary unit 20 was thermal domain.In addition, Indoor Thermal exchange temperature sensor 32 is configured in the heat-transfer pipe of the pars intermedia of indoor heat converter 14.Therefore, near the pars intermedia of indoor heat converter 14, the condensation temperature under refrigeration can being detected and heating running or evaporating temperature.
As shown in Figure 4, the motor 16a of compressor 10, cross valve 11, expansion valve 13, drive chamber's internal fan 16, evaporating temperature sensor 30, indoor temperature transmitter 31 are connected with the control part of air conditioner 1 with Indoor Thermal exchange temperature sensor 32.Therefore, control part is according to the running controlling air conditioner 1 from the instruction (running starts to operate or the design temperature etc. of indoor temperature) of remote controller or the evaporating temperature detected by evaporating temperature sensor 30, the indoor temperature (sucking the temperature of air) detected by indoor temperature transmitter 31, the heat exchange medium temperature that detected by Indoor Thermal exchange temperature sensor 32.
And, according to air conditioner 1, under the dehumidifying operation mode of regulation, secondary unit 20 has the mistake thermal domain in the evaporation territory of liquid refrigerant evaporates and the downstream in evaporation territory, but control compressor 10 and expansion valve 13, the scope in this evaporation territory is changed according to load.Here, change according to load and refer to according to the heat being provided to evaporation territory and change, and determine heat according to such as indoor temperature (sucking the temperature of air) and indoor air quantity.In addition, load is corresponding with required dehumidifying effect (required refrigerating capacity), can detect load according to such as indoor temperature and differing from of design temperature.
Difference according to indoor temperature and design temperature controls compressor 10.Be controlled to like this: because when the difference of indoor temperature and design temperature is large, load is large, therefore the frequency of compressor 10 increases, and because when the difference of indoor temperature and design temperature is little, load is little, therefore the frequency of compressor 10 reduces.
Expansion valve 13 is controlled according to the evaporating temperature detected by evaporating temperature sensor 30.As mentioned above, under the controlled state of the frequency of compressor 10, the mode of the temperature in the prescribed limit (10 DEG C ~ 14 DEG C) becoming near target evaporating temperature (12 DEG C) to make evaporating temperature controls expansion valve 13.Preferably, the prescribed limit of this evaporating temperature does not depend on the frequency of compressor 10 and is controlled so as to fix.But, even if change a little due to frequency, as long as be in fact fixing, then no problem.
Like this, under the dehumidifying operation mode of regulation, by controlling compressor 10 and expansion valve 13 according to load, thus change the scope in evaporation territory of secondary unit 20, evaporating temperature can be made to become temperature in prescribed limit.
According to air conditioner 1, secondary unit 20 and preceding heat exchanger 21a have the heat-transfer pipe of 12 sections respectively.And, when under the dehumidifying operation mode specified, the hop count becoming evaporation territory of secondary unit 20 is the hop count of preceding heat exchanger 21a over half, due to the scope in the evaporation territory of secondary unit can be expanded fully, therefore, it is possible to tackle the variation of load fully.Particularly effective when load is large.
Fig. 5 shows changes in flow rate when to change aperture in expansion valve 13.The aperture of expansion valve 13 changes continuously according to the number of drive pulses of input.Further, along with aperture reduces, in the flow minimizing of the cold-producing medium that expansion valve 13 flows through.According to expansion valve 13, be buttoned-up status when aperture is t0, when aperture is between t0 to t1, along with aperture increases, flow increases according to the first gradient, and when aperture is between t1 to t2, along with aperture increases, flow increases according to the second gradient.Here, the first gradient is greater than the second gradient.
About the control in order to make the range in the evaporation territory of secondary unit 20 carry out, an example is described.Such as, under the dehumidifying operation mode of regulation, when the scope in the evaporation territory at secondary unit 20 is regulation area, load becomes large, the frequency of compressor 10 increases, and the aperture of expansion valve 13 becomes large.Therefore, the scope in the evaporation territory of secondary unit 20 becomes and is greater than regulation area, even if the air quantity be drawn in indoor set 2 is fixing, the actual air quantity by evaporation territory also increases.
On the other hand, under the dehumidifying operation mode of regulation, when the scope in the evaporation territory at secondary unit 20 is regulation area, load diminishes, the frequency of compressor 10 reduces, and the aperture of expansion valve 13 diminishes.Therefore, the scope in the evaporation territory of secondary unit 20 becomes and is less than regulation area, even if the air quantity be drawn in indoor set 2 is fixing, the actual air quantity by evaporation territory also reduces.
Action time operation (dehumidifying running starts to operate) that start running to utilizing the remote controller of air conditioner 1 to select dehumidifying running is described.According to air conditioner 1, when load is large when carrying out dehumidifying running and starting to operate, after starting cooling operation not starting dehumidifying running, be correspondingly switched to dehumidify with the reduction of load and operate.
Further, in air conditioner 1, the frequency of the compressor changed according to the difference corresponding to indoor temperature and design temperature detects load.Therefore, according to air conditioner 1, when the frequency of compressor is less than assigned frequency, little to load, when cooling operation, evaporating temperature uprises and the state that cannot dehumidify detects.In addition, according to air conditioner 1, in detection evaporating temperature (evaporating temperature detected by evaporating temperature sensor 30 or the heat exchange medium temperature handed over temperature sensor 32 by Indoor Thermal and detect), this evaporating temperature is lower than set point of temperature, even if owing to can dehumidify fully when cooling operation, be not therefore switched to dehumidifying running yet.Therefore, according to air conditioner 1, when compressor frequency is less than assigned frequency, evaporating temperature higher than set point of temperature, start dehumidifying running.
First, carrying out (step S1) when dehumidifying running starts to operate when utilizing remote controller, judging whether whether compressor frequency be less than assigned frequency, evaporating temperature higher than set point of temperature (step S2).Assigned frequency is the upper limiting frequency of dehumidifying operation mode.Set point of temperature is the dehumidifying limiting temperature of cooling operation.Further, when be judged as compressor frequency more than assigned frequency or evaporating temperature below set point of temperature (step S2: no), start cooling operation (step S3).Then, the judgement of step S2 is repeated.On the other hand, in step s 2, when being judged as that compressor frequency is less than assigned frequency, evaporating temperature higher than (step S2: yes) when set point of temperature, dehumidifying running (step S4) is started.
The feature > of the air conditioner of < present embodiment
Air conditioner 1 according to the present embodiment, when when carrying out dehumidifying running and starting to operate, load is large, even if because when cooling operation, the temperature of heat exchanger is also low, thus can dehumidify fully, therefore, by starting cooling operation, can carry out expeditiously dehumidifying and freezing simultaneously.Further, when indoor temperature reduce and load diminish time, when cooling operation, become because evaporating temperature uprises and cannot dehumidify, therefore at that time carve being switched to dehumidifying running.Thereby, it is possible to the impact making the COP for dehumidifying be deteriorated is Min..
In addition, air conditioner 1 according to the present embodiment, starting operation by dehumidifying running after starting cooling operation, in evaporating temperature lower than not being switched to dehumidifying running when set point of temperature.In this case, because evaporating temperature is lower than setting, also can dehumidify even if be not therefore switched to dehumidifying running from cooling operation.
Below with reference to the accompanying drawings embodiments of the present invention are illustrated, but should think that concrete structure is not limited to these embodiments.According to claims, scope of the present invention is not shown according to the explanation of above-mentioned embodiment, scope of the present invention also comprises the change in all implications with claims equalization and scope.
In the above-described embodiment, secondary unit and main heat exchanger also can be integrally constituted.Therefore, in this case, indoor heat converter is integrally constituted, and the most weather side of indoor heat converter is provided with the part corresponding with secondary unit, its downwind side is provided with the part corresponding with main heat exchanger.
In addition, in the above-described embodiment, the air conditioner of the running carried out under the dehumidifying operation mode and warming operation pattern of cooling operation pattern, regulation is illustrated, but also can is the air conditioner of the running carried out under adopting the method beyond the dehumidifying operation mode specified to carry out the dehumidifying operation mode of dehumidifying running.
Utilizability in industry
If use the present invention, then the impact that the COP for the running that dehumidifies can be made to be deteriorated is Min..
Label declaration
1 air conditioner;
2 indoor sets;
3 off-premises stations;
10 compressors;
12 outdoor heat converters;
13 expansion valves;
14 indoor heat converters;
16 indoor fans;
20 secondary units;
21 main heat exchangers.
Claims (4)
1. an air conditioner, it possesses refrigerant loop compressor, outdoor heat converter, expansion valve and indoor heat converter coupled together, carry out using whole described indoor heat converter as the cooling operation in evaporation territory with using a part for indoor heat converter as the dehumidifying running in evaporation territory, the feature of described air conditioner is
Load is large when starting running when selecting dehumidifying running, starting after cooling operation, being correspondingly switched to dehumidify with the reduction of load and operating.
2. air conditioner according to claim 1, is characterized in that,
Difference according to indoor temperature and design temperature detects load.
3. air conditioner according to claim 1 and 2, is characterized in that,
Frequency according to described compressor detects load.
4. an air conditioner, is characterized in that,
After beginning cooling operation, in evaporating temperature lower than not being switched to dehumidifying running when set point of temperature.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPJP2012-093125 | 2012-04-16 | ||
| JP2012093125A JP5533926B2 (en) | 2012-04-16 | 2012-04-16 | Air conditioner |
| JP2012-093125 | 2012-04-16 | ||
| PCT/JP2013/060368 WO2013157405A1 (en) | 2012-04-16 | 2013-04-04 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104246386A true CN104246386A (en) | 2014-12-24 |
| CN104246386B CN104246386B (en) | 2016-01-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380020042.5A Active CN104246386B (en) | 2012-04-16 | 2013-04-04 | Air conditioner |
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| Country | Link |
|---|---|
| US (1) | US9513041B2 (en) |
| EP (1) | EP2857767B1 (en) |
| JP (1) | JP5533926B2 (en) |
| CN (1) | CN104246386B (en) |
| AU (1) | AU2013250425B2 (en) |
| BR (1) | BR112014025647B1 (en) |
| ES (1) | ES2628489T3 (en) |
| MY (1) | MY175729A (en) |
| SG (1) | SG11201406662TA (en) |
| WO (1) | WO2013157405A1 (en) |
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| US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
| US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
| US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| JP6555456B1 (en) | 2017-12-18 | 2019-08-07 | ダイキン工業株式会社 | Composition comprising refrigerant, use thereof, refrigerator having the same, and method of operating the refrigerator |
| US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| CN111479910A (en) | 2017-12-18 | 2020-07-31 | 大金工业株式会社 | Refrigerating machine oil for refrigerant or refrigerant composition, method for using refrigerating machine oil, and use as refrigerating machine oil |
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Also Published As
| Publication number | Publication date |
|---|---|
| BR112014025647A2 (en) | 2017-07-04 |
| MY175729A (en) | 2020-07-07 |
| US20150068236A1 (en) | 2015-03-12 |
| WO2013157405A1 (en) | 2013-10-24 |
| JP2013221671A (en) | 2013-10-28 |
| AU2013250425A1 (en) | 2014-11-27 |
| JP5533926B2 (en) | 2014-06-25 |
| CN104246386B (en) | 2016-01-20 |
| US9513041B2 (en) | 2016-12-06 |
| ES2628489T3 (en) | 2017-08-03 |
| AU2013250425B2 (en) | 2015-09-03 |
| EP2857767A4 (en) | 2016-03-16 |
| SG11201406662TA (en) | 2014-11-27 |
| EP2857767B1 (en) | 2017-05-31 |
| EP2857767A1 (en) | 2015-04-08 |
| BR112014025647B1 (en) | 2022-02-15 |
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